JPH0673389U - Rotary compressor - Google Patents

Abstract

(57) [Abstract] [Purpose] The present invention aims to improve lubricity for vanes and prevent noise and vibration of the compressor. When the vane 8 is projected to some extent by the rotation of the rotor 6 and reaches the region where the refrigerant is compressed, the lubricating oil O in the vane back pressure chamber 22 is guided by the groove 30 to the gap t between the vanes 8 and the vanes 8 and the vanes 8. The side wall 9a, 9b of the groove 9 or the vane 8 and the bore inner peripheral surface 3a are lubricated.

Description

[Detailed description of the device]

[0001]

[Industrial applications]

 The present invention relates to a rotary compressor having improved vane sliding properties.

[0002]

[Prior art]

 As shown in FIGS. 9 and 10, a conventional rotary compressor used in an automobile air conditioner or the like clamps a cylinder 2 provided in a casing 1 between a front side block 4 and a rear side block 5, and tightens a tightening bolt. It is tightened by (not shown).

The rotor portion 6 housed in the bore 3 of the cylinder 2 has a rotor body 7 and a slide vane 8, and contacts the inner peripheral surface 3 a of the elliptical bore 3 at a contact point. It is rotatably installed. Five vane grooves 9 are radially formed in the rotor body 7, and slide vanes 8 are slidably provided in the vane grooves 9.

When the rotor portion 6 is rotated via the shaft 10 by a drive source (not shown), the slide vane 8 projects from the vane groove 9 by a centrifugal force or the like and slides along the inner peripheral surface 3 a of the bore 3. Then, the refrigerant that is a compressible fluid that has flowed in from the inflow port 11 of the casing 1 flows into the compression chamber C through the suction port 12 that is opened in the front side block 4. Here, the compression chamber C is defined by the contact points, the inner peripheral surface 3a of the bore 3, the side blocks 4, 5, the slide vanes 8 or the slide vanes 8.

The volume of the compression chamber C changes with the rotation of the rotor portion 6, and the cooling medium sealed inside is compressed. The compressed refrigerant is discharged from the discharge port 13 opened in the cylinder 2 against the discharge valve 14, collides with the oil separator 16 through the communication passage 15, and then flows out from the outlet 17 to the outside.

Lubricating oil is introduced into the vanes 8 by utilizing a pressure of a pump (not shown) or a refrigerant, and the lubricating oil between the vanes 8 and the side wall of the vane groove 9 or the inner peripheral surface 3 a of the bore 3 is introduced. Sliding is taking place. An appropriate back force is applied to the vane 8 from the vane groove 9 toward the inner peripheral surface 3a of the bore 3 by the lubricating oil pumped.

In the illustrated example, the lubricating oil O is gas-liquid separated by the refrigerant colliding with the oil separator 16 and stored in the lubricating oil storage portion 18 formed by the bottom portion of the casing 1 and the side block 5. However, since the liquid surface of the lubricating oil reservoir portion 18 is pressurized by the pressure of the refrigerant, the lubricating oil O passes through the lubricating oil passage 19 or 20 and a bearing, a mechanical seal, etc. 21) or the vane back pressure chamber 22, and lubricates the bearings 21, the slide vanes 8 and the vane grooves 9, the side blocks 4 and 5 and the side surfaces of the rotor portion 6, and the like.

[0008]

[Problems to be solved by the device]

 However, if the refrigerant returning from the evaporator has a high degree of superheat and returns in a gas state, or if the rotary compressor is rotating at a high speed, there is a risk of insufficient lubrication. When the degree of superheat of the refrigerant is high, the amount of lubricating oil contained in the intake gas is small, and when the rotary compressor is rotating at high speed, the sliding of the cylinder 2 and the vanes 8 is severe, and the amount of lubricating oil supplied is large. Will run out. In particular, when the supply amount of lubricating oil is insufficient in the compression process in which the temperature of the refrigerant rises, the frictional force between the vane 8 and the inner peripheral surface 3a of the bore 3 increases, and the tip of the vane and the inner peripheral surface 3a of the bore 3 contact each other. May increase the frictional resistance of not only the vane 8 but also the inner peripheral surface 3a of the bore. As a result, the durability of the rotary compressor may decrease, and the vane 8 and the inner peripheral surface 3a of the bore 3 may not be smooth. Since no contact is made, abnormal noise or vibration may occur in the compressor. Further, when the pressure in the compression chamber C reaches the value at which the discharge valve 14 is opened, the lubricating oil in the compression chamber C also flows out together with the cooling medium, so that the lubricating oil flow into the vane groove 9 is reduced.

In order to make the rotary compressor operate smoothly, a lubricating oil is supplied along the surface of the cylinder (Japanese Utility Model Laid-Open No. 2-103,190) or a gear pump is used. To improve lubricity (Japanese Utility Model Laid-Open No. 52-41, 512) and one utilizing sliding movement of vanes (Japanese Utility Model Laid-Open No. 50-88, 907). All of them lack the certainty of discharging the lubricating oil to a predetermined position, and the lubrication of the contact portion between the vane and the inner peripheral surface of the cylinder, which requires the lubricating oil most, is insufficient. Some vanes have an oil groove formed therein (Japanese Patent Laid-Open No. 1-100,397, etc.). However, when an oil groove is formed in the vane itself, all positions where the rotor is rotating are formed. That is, the vane having the oil groove slides on the side wall of the vane groove in the entire rotation range, which is disadvantageous in terms of wear resistance. Moreover, as a result of the lubricating action being performed in the entire rotation range of the rotor, it is not possible to lubricate only the region where the lubricating oil is required, for example, the region that is in the compression process where the temperature of the refrigerant rises. There is a risk of this occurring, and the compression pressure escapes, resulting in poor efficiency.

The present invention has been made in view of the above problems of the prior art, and makes it easier for the lubricating oil in the vane back pressure chamber to enter the vane groove in the region where the vane needs the most lubricating oil. The purpose of the present invention is to provide a rotary compressor with less noise and vibration by improving the lubrication of the contact area between the vane and the inner peripheral surface of the cylinder to ensure smooth operation of the vane and reduce wear on the inner peripheral surface of the cylinder. To do.

[0011]

[Means for Solving the Problems]

 The present invention for achieving the above-mentioned object includes a cylinder (2) closed by both side blocks (4,5), a rotor (6) provided in a bore (3) of the cylinder (2), and a rotor (6). The vanes (8) slidably installed in the vane grooves (9) formed in (6), the lubricating oil passages (19) provided in the side blocks (4,5), and the lubrication It has a vane back pressure chamber (22) communicating with the oil passage (19) to guide the lubricating oil (O) to the base of the vane groove (9), and the vane groove (22) is rotated as the rotor (6) rotates. The vane (8) is projected and retracted from the (9), and the volume of the compression chamber (C) defined by the inner peripheral surface (3a) of the cylinder (2), both side blocks (4,5) and the vane (8) is divided. In the rotary compressor that is variable and discharges the compressed fluid compressed in this compression chamber (C) to the outside from the discharge port (17), the lubricating oil (O) in the compression chamber (C) is Lead to the gap (t) in the vane (8) The rotary compressor is characterized in that the groove portion (30) is formed in the side wall (9a, 9b) of the vane groove (9) and / or the side block (4,5). In particular, the groove portion (30) formed on the side walls (9a, 9b) of the vane groove (9) is preferably provided on the front side in the rotation direction of the rotor.

[0012]

[Action]

 In the rotary compressor of the present invention, when the rotor rotates and reaches a region where the vanes protrude to some extent and then compresses the refrigerant, the vane gap is communicated with the vane back pressure chamber by the side wall of the vane groove or the groove formed in the side block. It will be in the state of being. As a result, the lubricating oil in the compression chamber enters the gap between the vanes through this groove portion and lubricates between the vane and the side wall of the vane groove. As a result, the vanes and the vane grooves are lubricated, and smooth operation is achieved. In particular, even when the refrigerant with a high degree of superheat and a small amount of lubricating oil returns, or when the rotary compressor rotates at high speed and the sliding between the cylinder and the vane is severe, the compressed refrigerant is also discharged. While running, there will be no shortage of lubricating oil, smooth operation will be achieved, wear of the vane or cylinder inner peripheral surface will be suppressed, and noise and vibration will be greatly reduced.

[0013]

【Example】

 An embodiment of the present invention will be described below with reference to the drawings. 1 is a sectional view of a rotary compressor according to an embodiment of the present invention at right angles to an axis, FIG. 2 is a sectional equivalent view taken along line 2-2 of FIG. 1, and FIG. 3 is an enlarged sectional view of an essential part of FIG. 4 is an equivalent view taken along the line 3-3 of FIG. 4, FIG. 4 is an enlarged cross-sectional view of the main part of FIG. 2, and FIG. 5 is a graph showing the relationship between the rotation angle of the rotor and the pressure in the cylinder chamber. The same members as the members shown in FIG.

In the rotary compressor shown in FIGS. 1 and 2, a lubricating oil passage 19 or 20 is formed in the front side block 4 and the rear side block 5. One end of the lubricating oil passage 19 communicates with the lubricating oil reservoir 18 and the other end communicates with the vane back pressure chamber 22. The vane back pressure chamber 22 is formed in the front side block 4 and the rear side block 5 and communicates with the base of a plurality of vane grooves 9 respectively.

Particularly, in this embodiment, as shown in FIG. 3, a groove portion 30 for guiding the lubricating oil in the compression chamber C to the side wall of the vane groove 9 between the vane 8 and the side walls 9 a and 9 b of the vane groove 9. Has been formed. As shown in FIG. 2, the groove portion 30 is a side wall 9a of the vane groove 9 on the front side (hereinafter simply referred to as the front side and the opposite side is referred to as the rear side) in the direction in which the rotor 6 rotates (arrow in the figure). It is formed by making a hole near the vane back pressure chamber 22.

Generally, the compressor needs the most lubricating oil in the compression process where the temperature of the refrigerant becomes high. The vane 8 starts to project as the rotor 6 rotates, but when the lower end of the vane 8 is still at the base of the vane groove 9, compression is hardly performed and the temperature of the refrigerant is not yet high. When the rotor further rotates, the lower end of the vane 8 disengages from the base of the vane groove 9, moves into the vane groove 9, the refrigerant is compressed, and the temperature of the refrigerant also rises. Until the pressure in the compression chamber C is substantially equal to the back pressure Pv of the vane 8, there is no problem because the friction between the vane 8 and the inner peripheral surface 3a of the bore 3 is not large, and there is no problem. Is supplied. However, when the vane 8 has passed the state in which it protrudes outward in the radial direction in the vane groove 9 to the maximum extent, and gradually begins to retreat, the pressure in the compression chamber C gradually increases. Particularly, when the pressure is close to the average pressure Pd at the outlet of the compressor, the friction between the vane 8 and the inner peripheral surface 3a of the bore also increases, and lubricating oil is required. At this position, the vane 8 is in a state where the lower end A of the front end face 8a of the vane 8 contacts the front side wall 9a of the vane groove 9 and the point B of the rear end face 8b is as shown in FIG. It comes into contact with the rear side wall 9b of the vane groove 9. However, since the lubricating oil supplied in a pressurized state into the compression chamber C tends to flow to the back pressure chamber side by the groove portion 30, it passes around the lower end A and the side walls of the vane 8 and the vane groove 9. 9a is guided to a clearance t (hereinafter, a clearance of the vane). That is, the groove portion 30 functions as a communication passage that connects the base portion of the vane groove 9 and the gap t of the vane 8 when the lower end of the vane 8 separates from the base portion of the vane groove 9 and slightly moves in the vane groove 9. Will be done.

In FIG. 5, the rotation angle of the vane is θ, and the state where the vane is at the contact point is 0. Θ1 is the rotation angle when the refrigerant is pressurized to a pressure equal to the vane back pressure (Pv), θ2 is the rotation angle when the compressor has an average discharge pressure (Pd), θ3 is the maximum discharge Rotation angle at the time of reaching the pressure (Pd max), θ4; Rotation angle at the time when the discharge valve is closed and discharge is completed, θ5: Rotation angle at the time when the refrigerant becomes a pressure equal to the back pressure Pv of the vane, Then, the vane 8 starts to project after a while from the rotation angle 0, and when the rotation angle of the vane 8 becomes θ2, as shown in FIG. 6, the vane 8 is slightly radially inward from the maximum projection state. The point A is substantially at the outer end of the groove 30. Then, as the rotor 6 rotates, the vanes 8 move inward in the radial direction. When the rotation angle of the vane 8 becomes θ4, as shown in FIG. 7, the refrigerant is discharged from the refrigerant discharge port 13 and the compression is almost completed, and the vane 8 is located almost at the innermost end. When the vane 8 moves in the vane groove 9 within the range of the rotation angles θ2 to 4 as described above, it is preferable that the lubricating oil in the compression chamber C flows through the groove portion 30 into the gap t of the vane. This range is a zone where the discharge valve is open and compressed refrigerant is being discharged. In the vane groove 9, when it is receding inward in the radial direction, the lubricating oil also flows out together with the refrigerant. There is a shortage of lubricating oil that flows from the compression chamber C to the back of the vane.

During such a compression process, the vane 8 is inclined backward as shown in FIG. 4, so that the groove portion 30 allows the lubricating oil to easily flow from the compression chamber C into the vane groove 9, and Can be lubricated. The groove portions 30 are provided at a plurality of positions on the front side in the rotation direction of the rotor 6.

Next, the operation of the embodiment will be described. When the rotor portion 6 rotates via the shaft 10 by a drive source (not shown), the slide vane 8 projects from the vane groove 9 by the centrifugal force and an appropriate back force, and slides along the inner peripheral surface 3a of the bore 3. To do. Then, the refrigerant flowing from the inflow port 11 of the casing 1 is introduced into the compression chamber C through the suction port 12 formed in the front side block 4.

Since the volume of the compression chamber C changes with the rotation of the rotor portion 6, the refrigerant sealed inside is compressed and, after being compressed, is discharged from the discharge port 13 formed in the cylinder 2 to the discharge valve. It is discharged against 14 and collides with the oil separator 16 through the communication passage 15 and then flows out from the outlet 17 to the outside.

In this case, the lubricating oil O stored in the lubricating oil storage portion 18 formed by the bottom portion of the casing 1 and the side block 5 is pressurized by the discharged refrigerant, and the lubricating oil passage 19 or 20. Through the bearing 21 or the vane back pressure chamber 22 to lubricate the bearing 21 or the slide vane 8 and the vane groove 9.

In the present embodiment, since the lubricating oil O stored in the lubricating oil storage portion 18 is also introduced into the vane back pressure chamber 22, this lubricating oil O is supplied to the gap t of the vane 8. It

In this case, the vane 8 is positioned near the outer end of the groove portion 30 at the rotation angle θ 2 when the pressure of the refrigerant becomes the average discharge pressure (Pd) of the compressor, which is higher than the back pressure chamber pressure. is doing. When moving inward from here, the lubricating oil in the compression chamber C flows through the groove 30 to the vane back pressure chamber and is supplied to the gap t between the vane 8 and the vane groove 9. Therefore, this lubricating oil smoothly enters the gap t of the vane 8 and lubricates between the vane 8 and the vane groove 9. The lubricating oil passes through the discharge port 13 and continues until the rotation angle θ4 when the discharge valve is closed.

As described above, when the vane 8 is in the specific range of the rotation angles θ2 to θ4 where the discharge valve is open, the lubricating oil is supplied from the compression chamber C due to the groove portion 30. Since the lubricating oil is guided to the gap t of the vane 8 during this time, the supply amount of the lubricating oil does not become insufficient even in the compression process in which the temperature of the refrigerant rises, and the vane 8 and The sliding frictional resistance with the vane groove 9 does not increase, the vanes 8 and the like do not wear, the durability is improved, and abnormal noise and vibration are reduced. In particular, when the groove portions 30 are provided at a plurality of positions on the front side in the rotation direction of the rotor 6, the entire vane groove can be uniformly lubricated.

The present invention is not limited to the above-described embodiments, but can be variously modified within the scope of the utility model registration claim. For example, the groove portion 30 is not limited to the case described above, and may be formed on the side wall 9a on the rear side of the vane groove 9. In this case, although the lubricating oil may be hard to flow to the tip of the vane 8 due to the contact at the point B, the lubricating oil is sufficiently guided to the gap t of the vane 8. Further, as shown in FIG. 8, the groove portion 30a may be formed in the side blocks 4 and 5. Also in this case, the groove portion 30a connects the vane gap and the vane back pressure chamber 22 between the rotation angles θ2 to θ4 of the vane 8.

[0026]

[Effect of device]

 As described above, according to the present invention, when the vane lubrication reaches the region where the refrigerant is discharged, the gap of the vane is communicated with the vane back pressure chamber by the groove formed at the base of the vane groove, and the compression is performed. Lubricating oil in the room flows through this groove to the back pressure chamber of the vane and lubricates between the vane and the side wall of the vane groove, so the lubricity of the vane is improved and the operation of the vane is smooth. As a result, wear of the vane or the inner surface of the cylinder is suppressed, and noise and vibration are greatly reduced.

[Brief description of drawings]

FIG. 1 is a sectional view showing an embodiment of the present invention.

FIG. 2 is a sectional equivalent view taken along line 2-2 of FIG.

FIG. 3 is a view corresponding to an arrow along line 3-3 in FIG. 4, showing a main part of FIG.

FIG. 4 is an enlarged cross-sectional view of a main part of FIG.

FIG. 5 is a graph showing the relationship between the rotation angle of the rotor and the pressure in the cylinder chamber.

FIG. 6 is a cross-sectional view showing a vane state of a rotation angle θ2 of a rotor.

FIG. 7 is a cross-sectional view showing a vane state with a rotation angle θ4 of the rotor.

FIG. 8 is a cross-sectional view showing another embodiment of the present invention.

FIG. 9 is a cross-sectional view showing a conventional rotary compressor.

10 is a sectional view taken along the line 10-10 in FIG.

[Explanation of symbols]

2 ... Cylinder, 3 ... Bore,
3a ... inner surface of bore, 4 ... front side block, 5 ... rear side block,
6 ... rotor, 8 ... vane,
9 ... Vane groove, 9a, 9b ... Side wall,
17 ... Discharge port, 19 ... Lubricating oil passage,
22 ... Vane back pressure chamber, 30 ... Groove part,
C ... Compression chamber, O ... Lubricant, t ... Vane gap.

Front page continued (72) Inventor Junichi Asai 4-3-1 Yashiki, Narashino City, Chiba Seiko Seiki Co., Ltd.

Claims (2)

[Scope of utility model registration request] 1. A cylinder (2) closed by both side blocks (4,5), a rotor (6) provided in a bore (3) of the cylinder (2), and a rotor (6). The vanes (8) slidably provided in the vane groove (9), the lubricating oil passages (19) provided in the side blocks (4,5), and the lubricating oil passages (19) communicate with each other. The rotor (6) having a vane back pressure chamber (22) for guiding the lubricating oil (O) to the base of the vane groove (9).
The vane (8) is retracted from the vane groove (9) along with the rotation of the cylinder, and the inner peripheral surface (3a) of the cylinder (2) bore and both side blocks
Compression chamber (C) defined by (4,5) and vanes (8)
In the rotary compressor in which the volume of is compressed and the compressed fluid compressed in this compression chamber (C) is discharged from the discharge port (17) to the outside, the lubricating oil in the compression chamber (C)
A groove portion (30) for guiding (O) to the gap (t) of the vane (8) is formed on the side wall (9a, 9b) of the vane groove (9) and / or the side block (4,5). And a rotary compressor. 2. The rotary compressor according to claim 1, wherein the groove portion (30) formed on the side wall of the vane groove (9) is provided on the front side in the rotation direction of the rotor (6).